EP2428647B1 - Transitional Region for a Combustion Chamber of a Gas Turbine - Google Patents

Description

TECHNICAL AREA

The present invention relates to a gas turbine, in particular a special embodiment of the transition region between a combustion chamber and a turbine in a gas turbine.

STATE OF THE ART

Gas turbine may be configured with a single combustion chamber, but they may also have a so-called sequential combustion. In the latter, fuel is burned in a first combustion chamber and the combustion air is subsequently expanded via a first turbine, a high-pressure turbine. Behind the high-pressure turbine, the still hot combustion gases flow through a secondary combustion chamber in which fuel is again supplied and burned under auto-ignition. Behind this secondary combustion chamber, a low-pressure turbine is arranged, through which the combustion gases are expanded, optionally followed by a heat recovery system with steam generation.

The transition from combustion chamber to turbine is a critical area, because there are particularly complex temperature and pressure conditions in this. Typically, the combustion chamber, which is designed for example as an annular combustion chamber, has a somewhat shell-shaped outer boundary, an outer wall which consists of a heat-resistant material or is correspondingly coated, and which is normally composed of individual segments. On the opposite, closer to the axis inside there is a correspondingly formed inner boundary, an inner wall of corresponding materials.

The turbine in turn has a number of alternating rows of vanes and blades. The first row of blades arranged immediately behind the combustion chamber is typically a row of blades with considerable rotation of the blades with respect to the main axis direction. The guide vanes are typically designed as segment modules, in which each vane on the inside has an inner platform and on the outside an outer platform, and these platforms then with their inner surface and the flow channel of the combustion air radially inside or radially outside limit. Accordingly, on the radially inner side of the annular flow passage, there is a gap between the inner combustion heat shield (wall segment of the combustion chamber) and the inner stage of the first guide blade row, and on the radially outer side, a gap between the outer combustion heat shield (wall segment of the combustion chamber) and the outer Platform of the first vane row.

From the US 2009/0293488 It is known that it is possible to close this transition region substantially by a very small gap and additionally provide specific structures which ensure optimum cooling of the wall regions in this area. The problem with this approach, however, is that the required clearance between the combustion chamber module and the turbine is not readily ensured by the correspondingly small gap size.

Due to the different mechanical and thermal loads of the components combustion chamber and turbine but this gap must have a certain width and can not be easily closed or completely bridged.

In fact, the thermal expansion of the different contiguous components in this region (turbine, combustor) is very different and, in absolute terms, large due to the size of the component. There are correspondingly large gaps at the interfaces which must have sufficient gap widths over the entire transient course (for example hot restart). As a consequence, the gap width is and must be e.g. be greater at the base load point than is necessary for the driving condition. Accordingly, the problem can not be solved easily by reducing the gap width.

Furthermore, there are differences in the components and their influence by the flow processes. In particular, there are only small ones in the combustion chamber Pressure differences, while there are large pressure differences in the area of the turbine blades, which produce the pressure field. The pressure field acts on the column. The hot gas bearing parts outside the flow path must be protected from hot gas. Pressure peaks of the pressure field determine the pressure that must be available in the adjacent cavities. Leakage and higher RTDF (radial temperature distribution function) / emissions are the result. The flushing of the cavities is determined concretely by the occurring pressure peaks, and not by the medium pressure.

The problem with this gap, which forms a cavity pointing away from the hot gas duct into further structural components of the housing, is therefore also the fact that it is also exposed to complex flow conditions, in particular in the area of one guide vane. At the leading edge of the guide vanes, a so-called bow wave forms, which causes hot combustion air in the wall region to be pressed under pressure into this cavity and penetrates deep into it. This can give rise to problems in connection with overheating but also with oxidation of the corresponding surfaces.

In addition, the bending moment loads on the blades occur at the transitions between platform and profile. These bending moments in combination with the thermal stresses limit the size of the platforms and therefore the distance in which the gaps can be placed away from the tread dew points. In other words, the platform overhangs are limited.

From the EP 1 270 874 a gas turbine with a combustion chamber, a turbine and a transfer channel is known, which connects the outlet of the combustion chamber with a circular cross-section gas channel of the turbine.

PRESENTATION OF THE INVENTION

The present invention is intended to solve the disadvantages explained in the introduction in connection with said gap just upstream of the first row of guide blades, that is, in the transition from the combustion chamber to the first row of guide blades. Specifically, this involves the improvement of a gas turbine with a combustion chamber and a first Leitschaufelreihe arranged substantially immediately downstream therefrom wherein the radially outer side and / or radially inner boundary of the combustion chamber by at least one outer respectively inner heat shield (which, so to speak, the Inner wall of the combustion chamber forms and is typically formed in the form of one or more plates with a thermal protection layer; Also referred to as a heat shield segment) is formed, which at least one radially outward or radial is fixed within arranged combustion chamber structure, and wherein the flow path of the hot gases in the region of the guide vane row radially outer side or radially inwardly bounded by an outer or inner blade platform, which is at least indirectly attached to at least one turbine carrier. In other words, it is in particular in an annular combustion chamber to improve the design either on the hub side (radially inside wall boundary of the combustion chamber) or on the outside (radially outer side wall boundary of the combustion chamber), or both.

In contrast to solutions which simply aim to reduce the gap size, to reduce the entry of hot gas into the gap, or to cover the gap to some extent, the present invention makes the way basically to move the gap to a less critical location as it were. The most critical location is, as explained above, where it is conventionally located, at the upstream end of the blade platform, which typically is made as short as possible to minimize stress. Especially at this end of the platform, the influence of the leading edge of the first vane row on the flow and pressure distribution is large, which is why the above problems are present exactly in the gap area.

According to the present invention, the procedure is such that a plurality of plate-shaped heat shields are arranged at least indirectly on the turbine carrier upstream of the first guide blade row and substantially adjacent to the blade platform. So they lie in the direction of flow between the heat shield of the combustion chamber (also called combustion chamber heat shield) and the blade platform. These mini heat shields span this area over a certain axial distance, being shaped to form a flow wall adapted to the flow between the heat shield and the platform. The above-mentioned and required for the compensation of the thermal expansion differences gap between the combustion chamber and the turbine is thus shifted to some extent upstream and removed from the critical point immediately at the leading edge of the first row of vanes, or at least moved away. Specifically, this gap is in a more upstream area between This mini heat shield and the heat shield in the form of an upstream gap postponed.

A first embodiment of this embodiment of a gas turbine according to the invention is characterized in that the mini heat shields are attached to an extension of the turbine carrier which extends upstream with respect to the flow direction of the hot gases. In this embodiment, so to speak, the turbine carrier is extended somewhat upstream in the axial direction compared to the conventional construction, in order to attach to this extension, the mini heat shield can. Since this extension is thus to some extent part of the turbine, and is also exposed to the corresponding thermal expansion conditions, then the gap between the attached miniature heat shield and the adjacent blade platform can be set extremely low.

For assembly reasons, it may be advantageous not to extend the turbine support upstream of the original Mass, but to attach an additional element to the actual carrier. Accordingly, according to a further embodiment according to the invention, the procedure is such that the miniature heat shields are attached to at least one additional turbine carrier element arranged upstream of the turbine carrier and fastened thereto. In this embodiment, according to the turbine carrier does not need to be modified, but the attachment is ensured by a separate additional turbine support member which is mounted upstream of the turbine carrier. In other words, in this case, the mini heat shield is not directly but indirectly attached to the turbine carrier.

Between these heat shields then typically substantially axially extending gaps are present. These, to a certain extent, the heat shields arranged adjacent to one another around the circumference do not necessarily have to run axially, but can also be adapted quite specifically to the flow direction of the hot gases in this area. For example, these gaps can be arranged exactly parallel to the flow direction of the hot gases, which is often helical in this region, in this region, but they can also be arranged perpendicular thereto or below a certain one preferred angle. In general, means may be provided for applying a cooling air flow to these gaps, and / or seals may be provided in these gaps be provided. Also, such gaps can to some extent be avoided by the individual heat shields, for example, in the form of a groove / comb mesh or the like, as it is known from US2009 / 0293488 is known.

A further preferred embodiment is characterized in that contour of the annulus formed by the mini heat shields is not circular over its entire axial extent, but starting from the circular shape locally slight bulges are provided normal to the direction of the hot gas flow to locally increase the static pressure or to reduce and thus overall the uniformity of the static pressure distribution in the circumferential direction in the region of the gap to improve. Such bumps are for platforms of static turbine blades from the application with application number EP 09159355.8 known.

A further preferred embodiment is characterized in that between the blade platform and the at least one mini heat shield there is a substantially circumferential gap with a small gap width, that is, which preferably has a gap width in the axial direction in the range of 0.1-20 mm. For small industrial gas turbines and aeroderivatives, the gap width is typically 0.1 to 5 mm, for large gas turbines it is 0.5 to 20 mm. A large gas turbine is typically considered to be a gas turbine with a capacity of 50 MW. Here too, preferred means may be provided for applying a cooling air flow to this circumferential gap, and / or seals, for example labyrinth seals or even meshing with the blade platform may be provided.

In order to ensure a sufficient distance from the critical inflow edge of the first row of guide vanes, the procedure is preferably such that the miniature heat shield has a length in the axial direction in the range from 5 to 500 mm. For small industrial gas turbines and aeroderivatives the length is typically 5 to 50 mm, for large gas turbines it is 10 to 350 mm. For future very large gas turbines, lengths of up to 500 mm are conceivable. In other words, about that distance, the column which is very wide in the prior art construction is displaced upstream.

The critical gap of the prior art is typically in a region where the wall for the flow gases is substantially cylindrical.

The upstream gap can now typically be arranged at a location in which the wall of the combustion chamber is arranged conically tapered farther upstream in the flow direction, and it preferably has a gap in the radial direction in the range of about 0.1-20 mm. For small industrial gas turbines and so-called aeroderivatives (aircraft engine that was taken over and changed for industrial purposes), the gap width is typically 0.1 to 5 mm, for large gas turbines it is 0.5 to 15 mm and can be 20 mm or more for very large gas turbines.

A further preferred embodiment is characterized in that means are provided to apply cooling air to the upstream gap, and in particular to a cavity arranged behind it. In addition, at least one step element can be arranged in the inlet region of such a cavity, which reduces the width of the cavity by at least 10% in at least one step substantially perpendicular to the direction of flow of the hot gas in the cavity, preferably such a step element with respect to the axis of the turbine is formed circumferentially.

It is possible to design the entire construction so that a mini heat shield is arranged in the combustion chamber per burner, it is also possible to arrange, for example, two or three heat shields per burner, or a common heat shield for each burner or three burners. Typically, the number of combustor heat shields is selected to be an integer multiple of the number of mini heat shields, or the number of mini heat shields is selected to be an integer multiple of the number of combustor heat shields. For example, with a gas turbine of the type GT 24 with sequential combustion distributed around the circumference of the annular combustion chamber 24 burners, so it may be 24 mini heat shields distributed in such a construction around the circumference, that is a heat shield per burner, or even 12, so that two burners share a heat shield to some extent, or 48, if in each case two miniature heat shields are provided per burner.

Typically, there are significantly more vanes in the first row of vanes of the turbine than there are burners. It is also possible to adapt the number of heat shields to the conditions of the first row of guide vanes. Accordingly, it is possible that in each case a mini heat shield is arranged per guide vane of the first row of vane in the combustion chamber. It is also possible that in each case two vanes have a common heat shield upstream.

Typically, the number of vanes of the first row of vanes is selected to be an integer multiple of the number of mini heat shields or the number of mini heat shields is selected to be an integer multiple of the number of vanes of the first row of vanes.

These heat shields, whether their number is provided in relation to the burners or the guide vanes, can either be arranged exactly staggered or are preferably arranged such that the gaps existing between the heat shields are staggered between two adjacent burners respectively between two adjacent vanes are, since then those between the heat shields existing column are least loaded

The miniature heat shields are typically formed as individual, adapted to the flow shape substantially plate-shaped heat accumulation elements, which are attached via positive and / or non-positive and / or cohesive means to an upstream extension of the turbine carrier or on an attached to the turbine support additional turbine support member.

The heat shields usually have at least on the side facing the hot gases flowing in the combustion chamber on a heat insulating layer, which is for example a ceramic layer

The upstream gap typically transitions into a cavity on the rear side facing away from the combustion chamber, and this cavity can then extend, for example, in a substantially axial direction, for example in the form of a gap which essentially surrounds the axis of the gas turbine and forms a cylinder jacket.

Alternatively, it is possible that the upstream gap merges into a cavity on the rear side facing away from the combustion chamber, and that this cavity extends substantially in the radial direction, that is, for example, in the form of a substantially circulating around the axis of the gas turbine, so to speak, a circular disk forming gap.

But it is also possible that the gap has a course direction between these two directions (axial / radial).

Further embodiments are given in the dependent claims.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1

einen schematischen axialen Schnitt durch den radial äußeren Strömungsbereich beim Austritt der Brennkammer, das heißt beim Übergangsbereich von der Brennkammer zur ersten Leitschaufelreihe, bei einer Konstruktion nach dem Stand der Technik;

Fig. 2

einen schematischen axialen Schnitt durch den radial äußeren Strömungsbereich beim Austritt der Brennkammer bei einer Bauweise nach einem ersten Ausführungsbeispiel nach der Erfindung;

Fig. 3

einen schematischen axialen Schnitt durch den radial äußeren Strömungsbereich beim Austritt der Brennkammer bei einer Bauweise nach einem zweiten Ausführungsbeispiel nach der Erfindung; und

Fig. 4

einen schematischen axialen Schnitt durch den radial äußeren Strömungsbereich beim Austritt der Brennkammer bei einer Bauweise nach einem dritten Ausführungsbeispiel nach der Erfindung.

Preferred embodiments of the invention will be described below with reference to the drawings, which are given by way of illustration only and are not to be interpreted as limiting. In the drawings show:

Fig. 1

a schematic axial section through the radially outer flow region at the outlet of the combustion chamber, that is at the transition region from the combustion chamber to the first row of guide vanes, in a construction according to the prior art;

Fig. 2

a schematic axial section through the radially outer flow region at the outlet of the combustion chamber in a construction according to a first embodiment of the invention;

Fig. 3

a schematic axial section through the radially outer flow region at the outlet of the combustion chamber in a construction according to a second embodiment of the invention; and

Fig. 4

a schematic axial section through the radially outer flow region at the outlet of the combustion chamber in a construction according to a third embodiment of the invention.

DESCRIPTION OF PREFERRED EMBODIMENTS

In the following, it will be explained with reference to the figures how the transition region between the combustion chamber and the first row of guide vanes can be preferably configured. In connection with the figures which are now discussed, only the situation on the radial outside is presented in each case, but the considerations made here apply quite analogously also to the radial inner side, ie. for the hub-side wall boundary at the transition of the combustion chamber to the first row of guide blades.

FIG. 1 shows first the transition region of the wall from the combustion chamber 9 to the first row of guide blades 1 of the turbine 21 in a construction according to the prior art. The first vane row 1 is formed by typically individual ones Blade blades 2, which radially on the outside and radially inside have blade platforms 3. Via this blade platforms, which in turn form a closed circular ring which circumscribes the flow cross-section radially outwards, the row of guide blades 1 is fastened to a turbine carrier 4. Since high temperatures prevail here, there is a corresponding cooling air supply 5, which optionally open into corresponding cooling air ducts in the platforms 3 and / or the blades 2.

Upstream of this first row of guide vanes 1 is the combustion chamber 9 and this is typically limited by one or more heat shields 7 fixed to a combustion chamber structure 6. These heat shields 7 are typically plate-shaped and have thermal protection layers on the side exposed to the hot gases.

The hot gases flow, as is schematically indicated by the arrow 10, in a substantially axial direction downstream of the burner, which in FIG. 1 are not shown and to some extent lie on the right side of the area shown. These hot gases meet inter alia on the leading edge 12 of the blades 2. Straight in this area, but now the transition between the heat shield 7 and the platform 3, in this transition region a circumferential gap 8 is arranged, which opens behind it in a cavity 11, the extends deep into the supporting structure of the Turbinenträges 4 and the combustion chamber structure 6. This gap is required because of the effects mentioned above and is typically with a gap d in the range of 10 to 50 mm. If the gap is selected narrower, different thermal expansions of the components combustion chamber / turbine and other effects can not be compensated sufficiently. Accordingly, even in the area of this gap, a great deal of cooling or flushing of the cooling air is also required even at high pressure, since the components lying in the cavity 11 must be protected from the hot flow gases, and since at the same time high at this point Pressure fluctuations and especially high pressure peaks are present.

FIG. 2 now shows a first embodiment of the invention. Between the heat shield 7 and the first blade platform 3 of the first row of guide blades 1, an intermediate element in the form of a mini heat shield 13 is interposed. This heat shield 13 is doing directly to an upstream extension 4 'of the Turbine carrier 4 attached. It is to some extent mini-heat shields, which are arranged distributed around the circulation of the annular combustion chamber. These heat shields 13 may, as shown in this figure, be realized on the side of the guide vane row 1 via a connection with fastening projection 14 and retaining lug 15 and deck area 16 arranged above it, but other fastening possibilities can also be realized. Due to the fact that this additional heat shield is directly attached to the same support element, specifically to the turbine support 4, and accordingly exposed to essentially the same conditions as the blade platform 3 both in terms of vibration and thermal expansion, it is now possible to the corresponding gap dimension d of the remaining gap 23 between blade platform 3 and heat shield 13 extremely low, so here, for example, gap mass in the axial direction of 0.5 - 3 mm are possible without causing problems.

The gap 17 between the heat shield 7 and the heat shield 13 is now moved much further upstream, namely the upstream gap 17 is now also still arranged at the extended wall zone of the combustion chamber 9. In addition, the arranged behind this upstream gap 17 cavity 20 is no longer as in the prior art in the radial direction but as an axial cavity 20 'in the axial direction 25, which may have further advantages, in particular that this gap with a gap d' can be realized can, which is much lower than the gap, if the corresponding gap to some extent runs in the radial direction, as for example in Fig. 1 is shown.

A second embodiment is in FIG. 3 shown. An essential difference to the construction according to FIG. 2 (In the entirety of the figures, the same or functionally equivalent components are denoted by the same reference numerals) is that the turbine support 4 has no upstream extension 4 ', but that instead of an additional upstream turbine support member 18 has. This separate turbine carrier element 18 is attached to the turbine carrier 4, this can be done via a positive connection and / or a frictional connection and / or a material bond, for example, on the front side 19 of the turbine carrier. Basically, this additional turbine support element 18 performs the same function as the upstream extension of the turbine support. For assembly reasons, it may be advantageous not to the turbine support to the original Mass extend in the upstream direction, but an additional element, here just the additional turbine support member 18 to attach to the actual turbine support 4. A third embodiment is in FIG. 4 shown. Here, the additional mini heat shield 13 is also indirectly attached via an additional turbine support member 18 on the turbine carrier 4. Basically, by the way, this can be both in terms of construction FIG. 3 as well with FIG. 4 , the additional turbine support member 18 may be configured in the form of a circumferential ring, but it may also be segments, which do not even have to be adjacent to each other circumferentially, but which may also be distributed, for example, spaced around the circulation of the annular combustion chamber. In contrast to the embodiment according to FIG. 3 is with that after FIG. 4 the upstream gap 17 is slightly less advanced and also runs the gap 17 and the underlying cavity 20 here not in the axial direction, but al radial cavity 20 "in the radial direction.

The individual mini heatshields are distributed in some form of segments around the circumference of the annular combustion chamber in the form. The number of such heat shields can, as explained above, either depending on the number of burners, the number of combustion chamber heat shields or depending on the number of vanes 2 are selected. Between the individual heat shields or the segments of such heat shields usually remain axially extending column 24, which in FIG. 4 are indicated schematically by a dashed arrow. These axially extending gaps 24 are preferably, as well as possibly also the gaps 17 and 23, acted upon with cooling air, or with seals, such as labyrinth seals, provided to protect underlying components. As a result of the lower gap mass, generally lower pressures are required for the scavenging air, and generally less scavenging air or cooling air is required. In addition, due to the segment-like design of the individual mini heatshields can also be resorted to a local treatment of the pressure peaks. In general, the design makes it possible to build more compact turbines. LIST OF REFERENCE NUMBERS 1 first vane row 16 deck area 2 first vane row, airfoil 17 Gap at the upstream location 3 first vane row, vane platform 18 additional turbine carrier element 4 Turbine carrier (or turbine vane carrier) 19 Front of 4 20 Cavity behind 17 4 ' upstream extension of the turbine carrier 20 ' axial cavity 20 " radial cavity 5 Cooling air supply 21 turbine 6 Combustion chamber structure (suspension at the combustion chamber housing 22 gas turbine 23 Gap between 3 and 13 24 axially extending gap between distributed over the circumference adjacent heat shields 7 Combustion chamber heat shield, (heat shield of the combustion chamber) 8th Gap at the blade platform 25 axial direction 26 radial direction 9 combustion chamber 10 Flow direction of the hot gases d Gap in the blade platform 11 Cavity behind 8 d ' Gap in the upstream column 17 in the radial direction 12 leading edge 13 Mini heat shield, separate heat shield d " Gap in the upstream column 17 in the axial direction 14 fixing projection 15 retaining nose

Claims (13)

1. Gas turbine (22) with at least one combustion chamber (9) and a first guide vane row (2) of a turbine (21) arranged substantially immediately downstream thereof, wherein the radially outer and/or radially inner delimitation of the combustion chamber (9) is formed by at least one outer or inner heat shield (7) respectively which is attached to at least one combustion chamber structure (6) arranged radially outside or radially inside respectively, and wherein the flow path of the hot gases (10) in the region of the guide vane row (2) is delimited radially outwardly and/or radially inwardly by an outer or inner vane platform (3) respectively which is attached at least indirectly to at least one turbine carrier (4),
   characterised in that a plurality of platform-like mini heat shields (13) is arranged on a widening (4') of the turbine carrier (4) extending upstream, or on a turbine carrier element (18) arranged upstream of the turbine carrier (4) and attached thereto, upstream of the first guide vane row (2) and substantially adjacent to the vane platform (3) and in the flow direction (10) between the heat shield (7) and the vane platform (3), and between these, forming the flow wall, in the form of a course adapted to the flow,
   wherein an upstream gap (17) is present between the mini heat shields (13) and the heat shields (7).
2. Gas turbine (22) according to claim 1, characterised in that a plurality of mini heat shields (13) is arranged around the periphery of the wall of the combustion chamber (9), between which preferably substantially axial gaps (24) or gaps running substantially in the main flow direction (10) are present, wherein preferably means are provided for applying a cooling air flow to these gaps, and/or seals are provided in these gaps (24).
3. Gas turbine (22) according to any of the preceding claims, characterised in that a substantially circumferential gap (23) is present between the vane platform (3) and the mini heat shields (13), which gap preferably has a gap width (d) in the axial direction in the range from 1 - 5 mm, preferably in the range from 2 - 4 mm, wherein furthermore preferably means are provided which apply a cooling air flow to this circumferential gap (23).
4. Gas turbine (22) according to any of the preceding claims, characterised in that the mini heat shield (13) has a length in the axial direction (25) in the range from 5 - 500 mm, preferably in the range from 10 - 350 mm.
5. Gas turbine (22) according to any of the preceding claims, characterised in that the upstream gap (17) is arranged at a point at which the wall of the combustion chamber is arranged conically tapering, and wherein preferably the gap dimension (d') in the radial direction (26) preferably lies in the range from 0.1 - 20 mm, preferably in the range from 0.5 - 20 mm, and/or wherein preferably the gap dimension (d") in the axial direction (25) preferably lies in the range from 0.1 - 20 mm, preferably in the range from 0.5 - 20 mm.
6. Gas turbine (22) according to any of the preceding claims, characterised in that means are provided for applying cooling air to the upstream gap (17) and in particular to a cavity (20) arranged behind this, wherein preferably in the inlet area of such a cavity at least one step element is arranged which reduces the width of the cavity by at least 10% in at least one step running substantially perpendicular to the flow direction of the hot gas in the cavity (20), wherein preferably such a step element is configured circumferentially relative to the axis of the turbine.
7. Gas turbine (22) according to any of the preceding claims, characterised in that the number of combustion chamber heat shields (7) is an integral multiple of the number of mini heat shields (13), or the number of mini heat shields (13) is an integral multiple of the number of combustion chamber heat shields (7).
8. Gas turbine (22) according to any of the preceding claims, characterised in that the number of mini heat shields (13) is an integral multiple of the number of guide vanes (2) of the first guide vane row (13¹), or the number of guide vanes (2) of the first guide vane row is an integral multiple of the number of mini heat shields (13).
9. Gas turbine (22) according to any of the preceding claims, characterised in that the mini heat shields (13) are configured as individual heat build-up elements adapted to the flow form, which are attached to the extension (4') of the turbine carrier and/or to the additional turbine carrier element (18) attached to the turbine carrier (4) via form-fit and/or force-fit and/or material-fit means (14, 15).
10. Gas turbine (22) according to claim 11, characterised in that the heat shields (13) have a thermal barrier layer at least on the side facing the hot gases flowing into the combustion chamber.
11. Gas turbine (22) according to any of the preceding claims, characterised in that on the back side facing away from the combustion chamber (9), the upstream gap (17) transforms into a cavity (20), and that this cavity (20) extends substantially in the axial direction (25), preferably in the form of a gap (20') running substantially around the axis of the gas turbine (22) and forming a cylinder casing.
12. Gas turbine according to any of the preceding claims, characterised in that the contour of the ring chamber formed by the mini heat shields (13) is not circular over its entire axial extension, but starting from the circle form has slight local bulges which are normal to the direction of the hot gas flow (10), in order to increase or reduce the static pressure locally and hence as a whole improve the uniformity of the static pressure distribution in the circumferential direction in the region of the upstream gap (17).
13. Gas turbine according to any of the preceding claims, characterised in that on the back side facing away from the combustion chamber (9), the upstream gap (17) transforms into a cavity (20), and that this cavity (20) extends substantially in the radial direction (26), preferably in the form of a gap (20") running substantially around the axis of the gas turbine (22) and forming a circular disc.

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